Vertical bearing device

ABSTRACT

A lubricating oil passage portion that constitutes a cooling portion is exposed to the outside from a casing. Lubricating oil having absorbed heat of a thrust bearing portion and a journal bearing portion is cooled in the cooling portion, when the lubricating oil moves from an upper oil chamber to a lower oil chamber while circulating by use of gravity. Thus, the circulating lubricating oil prompts cooling of the heated thrust bearing portion and journal bearing portion. Additionally, the lubricating oil passage portion of the cooling portion is provided integrally with the casing, on the radially outer side of the casing.

CROSS-REFERENCE TO RELATED APPLICATIONS

This is a U.S. National Stage Patent Application from InternationalPatent Application No. PCT/JP2016/072378, filed on Jul. 29, 2016, whichis based on and claims priority to Japanese Patent Application No.2015-162026, filed on Aug. 19, 2015, the entire contents of both ofwhich are incorporated herein by reference.

FIELD OF THE INVENTION

The present invention relates to a vertical bearing device.

BACKGROUND OF THE INVENTION

A vertical bearing device that supports a rotating shaft member of arotary machine such as a large generator and electric motor is publiclyknown. The vertical bearing device supports both of thrust load in theaxial direction and radial load in the radial direction, of the rotatingshaft member that extends vertically in the direction of gravitationalforce. Bearing parts corresponding to axial and radial load of thevertical bearing device become heated by rotation of the rotating shaftmember, and therefore need to be appropriately cooled. Conventionally, avertical bearing device has been adopting an air cooler that cools thewhole device mainly by air-blowing, or an oil cooler that coolslubricating oil on the outside. When an air cooler is used, a fan thatrotates with the rotating shaft member is used to cool the bearingdevice by an air flow generated by the fan (Japanese Patent Laid-OpenNo, 2003-293977). Instead, when an oil cooler is used, a pump device orthe like for circulating lubricating oil is used to dischargelubricating oil that lubricates the bearing part to the outside, forexample, and the lubricating oil is circulated between the bearingdevice and the cooler to thereby cool the bearing device (JapanesePatent Laid-Open No. 5-106636).

However, since rotary machines to which the vertical bearing device isapplied are becoming larger and high-speed, the heat generated at thebearing parts also tends to increase. For this reason, the verticalbearing device is required to have higher cooling capacity. However,when an air cooler such as that described in Japanese Patent Laid-OpenNo. 2003-293977 is used, cooling capacity depends on air flow and thecontact area between the air flow and radiator fins that come intocontact therewith. In other words, to enhance cooling capacity, it isessential to enlarge the surface area of the radiator fins. Accordingly,improvement in cooling capacity causes a problem of enlargement ofradiator fins, and therefore enlargement of the vertical bearing deviceitself.

When an oil cooler is used, enlargement of the vertical bearing deviceitself can be avoided, but piping from the vertical beating device tothe external oil cooler is required. This complicates structure andmaintenance. Moreover, if a failure occurs in the function of the oilcooler or the piping, it becomes difficult to cool the vertical bearingdevice itself.

SUMMARY OF THE INVENTION

Hence, an objective of the present invention is to provide a verticalbearing device that has high cooling capacity, while preventingenlargement and complication of structure and maintenance.

In a vertical beating device, a container-shaped casing partitions anoil chamber into an upper oil chamber on the upper side and a lower oilchamber on the lower side in the direction of gravitational force, theoil chamber being formed by the casing and a base plate. A cooling parthas a lubricating oil passage part that allows passage of lubricatingoil moving from the upper oil chamber to the lower oil chamber.Lubricating oil stored in the upper oil chamber moves to the lower oilchamber in the direction of gravitational force, through the lubricatingoil passage part of the cooling part. The cooling part is exposed to theoutside from the casing. Hence, lubricating oil flowing through thecooling part loses heat in the cooling part exposed to the outside ofthe casing. Thus, lubricating oil having absorbed heat of a thrustbearing part and a journal bearing part is cooled in the cooling partwhile moving from the upper oil chamber to the lower oil chamber. As aresult, the circulating lubricating oil prompts cooling of the heatedthrust bearing part and journal bearing part. Additionally, the coolingpart is provided integrally with the casing, on the radially outer sideof the casing. For this reason, the cooling part does not require longpiping. In this way, cooling capacity can be improved while preventingcomplication of structure and maintenance.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic diagram of a section of a vertical bearing deviceof a first embodiment.

FIG. 2 is a diagram of a rotary machine to the vertical bearing deviceof the first embodiment is applied.

FIG. 3 is an arrow view as seen from an arrow III direction of FIG. 1.

FIG. 4 is an enlarged view enlarging the vicinity of an annular part ofthe vertical bearing device of FIG. 1.

FIG. 5 is a cross-sectional view of the annular part illustrated in FIG.4, cut along line V-V of FIG. 4.

FIG. 6 is an enlarged view enlarging the vicinity of a connection holeof the vertical bearing device illustrated in FIG. 4.

FIG. 7 is a cross-sectional view of a casing of the vertical bearingdevice of the first embodiment, cut along line VII-VII of FIG. 4.

FIG. 8 is a cross-sectional view of the vicinity of the connection holeof FIG. 7, cut along line of FIG. 7.

FIG. 9 is an enlarged view further enlarging the vicinity of the annularpart of the vertical bearing device illustrated in FIG. 4.

FIG. 10 is a cross-sectional view of the vicinity of a connection holeof a modification of the first embodiment, cut along a positioncorresponding to line VIII-VIII of FIG. 7.

FIG. 11 is a cross-sectional view of the vicinity of the connection holeof the modification of the first embodiment, cut along the positioncorresponding to line VIII-VIII of FIG. 7.

FIG. 12 is a cross-sectional view of a part of a casing and a coolingpart of a vertical bearing device of a second embodiment.

FIG. 13 is a cross-sectional view of a part of a casing and a coolingpart of a vertical bearing device of a modification of the secondembodiment.

FIG. 14 is a cross-sectional view of a part of a casing and a coolingpart of a vertical bearing device of a modification of the secondembodiment.

FIG. 15 is a cross-sectional view of a part of a casing and a coolingpart of a vertical bearing device of a modification of the secondembodiment.

FIG. 16 is a schematic diagram of a section of a vertical bearing deviceof a third embodiment.

FIG. 17 is a schematic diagram of a section of a vertical bearing deviceof a modification of the third embodiment.

FIG. 18 is a schematic diagram of a section of a vertical bearing deviceof a fourth embodiment.

FIG. 19 is a schematic diagram of a section of a vertical bearing deviceof a fifth embodiment.

FIG. 20 is a cross-sectional view of a part of a casing and a coolingpart of a vertical bearing device of a sixth embodiment.

FIG. 21 is a cross-sectional view of a part of a casing and a coolingpart of a vertical bearing device of another embodiment.

BRIEF DESCRIPTION OF EMBODIMENT(S) OF THE INVENTION

Hereinafter, vertical bearing devices of multiple embodiments will bedescribed on the basis of the drawings. Note that in the multipleembodiments, substantially common parts are assigned the same referencenumerals, and descriptions thereof will be omitted.

First Embodiment

A vertical bearing device 10 illustrated in FIGS. 1, 2, and 3 is used asa bearing of a rotary machine 11 illustrated in FIG. 2. The rotarymachine 11 includes a rotor 13 that rotates around a rotating shaftmember 12, such as a generator, pump, motor, and a turbine. The rotarymachine 11 is not limited to these examples, and may be applied to anydevice that rotates around a rotating shaft member 12. The rotarymachine 11 includes the rotating shaft member 12 at the center ofrotation. The rotating shaft member 12 extends vertically in thedirection of gravitational force. The vertical bearing device 10supports the rotating shaft member 12 of the rotary machine 11 at theupper end of the rotary machine 11, that is, on the upper side in thedirection of gravitational force. The vertical bearing device 10 isfixed on a floor 14 of a facility, and suspends and supports the rotarymachine 11. Note that the rotating shaft member 12 may penetrate thevertical bearing device 10 in the upper direction, and a drive sourcethat drives the rotating shaft member 12 may be provided above thevertical bearing device 10.

As illustrated in FIG. 1, the vertical bearing device 10 includes athrust collar 21, a base plate 22, a thrust bearing portion 23, a casing24, a journal bearing portion 25, and a cooling portion 26. The thrustcollar 21 is formed into a cylinder, and is provided integrally with therotating shaft member 12. Accordingly, the thrust collar 21 rotatesintegrally with the rotating shaft member 12. The thrust collar 21 hasan upper face portion 31, a cylinder portion 32, and an annular portion33. The upper face portion 31, cylinder portion 32, and annular portion33 are formed as one body. The upper face portion 31 is positioned atthe upper end of the thrust collar 21, and the rotating shaft member 12penetrates the center of the upper face portion 31. The cylinder portion32 extends downward from the upper face portion 31, and is provided onthe axially outer side of the rotating shaft member 12 as a cylinderthat is concentric with the rotating shaft member 12. The annularportion 33 is provided at the lower end of the cylinder portion 32, thatis, on an end part opposite to the upper face portion 31. The annularportion 33 has a larger outer diameter than the cylinder portion 32, andits end part on the outer peripheral side protrudes farther to theradially outer side than the cylinder portion 32. The annular portion 33has, in the radial direction of the rotating shaft member 12, an innerperipheral face 331 on the inner peripheral side and an outer peripheralface 332 on the outer peripheral side. The rotating shaft member 12 isassembled integrally with the thrust collar 21 by penetrating the upperface portion 31 of the thrust collar 21. The rotating shaft member 12 isfixed to the thrust collar 1 by press-fitting or welding, for example.

The base plate 22 has a main body 34 and an oil cylinder portion 35. Themain body 34 and the oil cylinder portion 35 of the base plate 22 areformed as individual members, or are formed as one body by a singlemember. In the embodiment, the oil cylinder portion 35 is formedseparately from the main body 34, and is attached to the main body 34.The main body 34 is formed into a circular plate having an opening 36 atthe center thereof. The rotating shaft member 12 penetrates the centeropening 36. The oil cylinder portion 35 is provided as a cylinder formedalong the edge of the opening 36 of the main body 34, and extends upwardfrom the main body 34. Hence, the oil cylinder portion 35 cylindricallysurrounds the radially outer side of the rotating shaft member 12. Thebase plate 22 is fixed to the floor 14 of the facility, or is fixed toan unillustrated housing or the like of the rotary machine 11.

The thrust bearing portion 23 is provided in a part where the thrustcollar 21 and the base plate 22 face each other. Specifically, thethrust bearing portion 23 is provided in a part where the thrust collar21 and the base plate 22 face each other in the axial direction of therotating shaft member 12. In the embodiment, the thrust bearing portion23 is provided in the main body 34 of the base plate 22, in a positionwhere it faces the annular portion 33 of the thrust collar 21. Thethrust bearing portion 23 slides on the annular portion 33 of the thrustcollar 21 that rotates together with the rotating shaft member 12. To bespecific, the thrust bearing portion 23 slides on a sliding surface 333on the main body 34 side of the annular portion 33. Thus, the thrusthearing portion 23 axially supports the rotation of the rotating shaftmember 12.

The casing 24 surrounds the outer peripheral side of the rotating shaftmember 12. The casing 24 has a casing main body 41, a middle wall 42, aninner wall 43, and a lower wall 44. The casing 24 is connected to thebase plate 22 on the lower end thereof. The casing 24 forms, togetherwith the base plate 22, a container having an open upper end. Thecontainer-like space formed of the casing 24 and the base plate 22 is anoil chamber 45 that stores lubricating oil. In other words, the casing24 is integrated with the base plate 22 to form a container, and formsthe oil chamber 45. The lubricating oil is filled in the oil chamber 45

The casing main body 41 is formed into an annular shape, and constitutesan outer wall of the casing 24. The lower end of the casing main body 41is in contact with the base plate 22. The middle wall 42 is provided inthe middle of the casing main body 41 in the axial direction, andprotrudes radially inward from the casing main body 41. That is, themiddle wall 42 protrudes to the rotating shaft member 12 side in anannual shape, from an inner wall of the casing main body 41. The innerwall 43 extends upward from the vicinity of a radially inner end part ofthe middle wall 42. The inner wall 43 is provided in a cylindrical shapein the vicinity of the radially inner end part of the middle wall 42.The lower wall 44 extends downward from the middle of the middle wall 42in the radial direction. As in the case of the inner wall 43, the lowerwall 44 is provided in a cylindrical shape below the middle wall 42.

Thus, the middle wall 42 of the casing 24 partitions the oil chamber 45formed with the base plate 22 into an upper oil chamber 46 and a loweroil chamber 47. The upper oil chamber 46 is formed into an annular shapebetween the casing main body 41 and the inner wall 43, on the upper sideof the middle wall 42. Meanwhile, the lower oil chamber 47 is formedinto an annular or cylindrical shape between the casing main body 41 andthe lower wall 44, on the lower side of the middle wall 42. As describedabove, the casing 24 uses the middle wall 42 to partition the oilchamber 45 into the upper oil chamber 46 on the upper side and the loweroil chamber 47 on the lower side in the direction of gravitationalforce. The casing 24 has a top plate 48. The top plate 48 covers theupper end side of the container-shaped oil chamber 45.

The journal bearing portion 25 is provided in a part where the thrustcollar 21 and the casing 24 face each other. Specifically, the journalbearing portion 25 is provided in a part where the thrust collar 21 andthe casing 24 face each other in the radial direction of the rotatingshaft member 12. In the embodiment, the journal bearing portion 25 isprovided on the inner wall 43 of the casing 24, in a position where itfaces the cylinder portion 32 of the thrust collar 21. The journalbearing portion 25 slides on the cylinder portion 32 of the thrustcollar 1 that rotates together with the rotating shaft member 12. To bespecific, the journal bearing portion 25 slides on an outer peripheralface of the cylinder portion 32. Thus, the journal bearing portion 25radially supports the rotation of the rotating shaft member 12.

The cooling portion 26 has a lubricating oil passage portion 51 and aradiating portion 52. The lubricating oil passage portion 51 isconfigured of a pipe-like member that allows passage of lubricating oil,and has a lubricating oil groove formed therein. The lubricating oilpassage portion 51 has one end connected to the upper oil chamber 46,and the other end connected to the lower oil chamber 47. Specifically,the lubricating oil passage portion 51 has an upper end part connectedto the upper oil chamber 46, and a lower end part connected to the loweroil chamber 47. The lubricating oil passage portion 51 is directlyattached to the casing main body 41. In other words, the lubricating oilpassage portion 51 is formed integrally with the casing main body 41.Moreover, the lubricating oil passage portion 51 protrudes radiallyoutward from the casing main body 41. That is, the lubricating oilpassage portion 51 is exposed to the outside from the casing main body41. The radiating portion 52 is provided in the lubricating oil passageportion 51 exposed from the casing main body 41. The radiating portion52 has unillustrated radiator fins and other parts to ensure surfacearea for heat exchange. As illustrated in FIG. 3, multiple coolingportions 26 are provided in the circumferential direction of thevertical bearing device 10. In the embodiment, the vertical bearingdevice 10 includes four cooling portions 26 equally spaced apart in thecircumferential direction. The number and arrangement of the coolingportions 26 are not limited to the example illustrated in FIG. 3, andmay be set arbitrarily.

Lubricating oil stored in the upper oil chamber 46 illustrated in FIG. 1flows to the lower oil chamber 47 on the lower side through thelubricating oil passage portion 51, due to gravity and a pumping effectcaused by circulation of the lubricating oil. At this time, lubricatingoil passes through the lubricating oil passage portion 51 exposed fromthe casing main body 41. Hence, lubrication oil loses heat in theradiating portion 52 disposed in the way of lubricating oil passageportion 51. That is, lubricating oil loses heat in the radiating portion52 while flowing from the upper oil chamber 46 to the lower oil chamber47 through the lubricating oil passage portion 51, and is cooled. As hasbeen described, the cooling portion 26 cools lubricating oil flowingfrom the upper oil chamber 46 to the lower oil chamber 47.

In addition to the above, the vertical bearing device 10 also includesan air blowing portion 53. The air blowing portion 53 has a fan portion54 that rotates together with the rotating shaft member 12. Rotation ofthe fan portion 54 together with the rotating shaft member 12 forms anup-to-down air flow on the outer side of the casing 24. The air flowmoves along the top plate 48 and the casing main body 41 of the casing24, and passes the radiating portion 52 of the cooling portion 26. Thus,the air flow formed by rotation of the fan portion 54 cools the casing24 and the cooling portion 26. Consequently, heat loss from lubricatingoil stored in the oil chamber 45 and lubricating oil passing through thecooling portion 26 is prompted. The casing 24 may have fins 49 in aposition where the air flow is formed by rotation of the fan portion 54.

The casing 24 partitions the oil chamber 45 not only into the upper oilchamber 46 and the lower oil chamber 47, but also into a circulation oilchamber 55. The circulation oil chamber 55 is formed in a part of theoil chamber 45 except for the upper oil chamber 46 and the lower oilchamber 47. The circulation oil chamber 55 accommodates a part of thecylinder portion 32 and the annular portion 33 of the thrust collar 21.Additionally, the thrust bearing portion 23 and the journal bearingportion 25 are provided in the circulation oil chamber 55. That is, thethrust bearing portion 23 that slides on the annular portion 33 of thethrust collar is positioned on the lower side of the circulation oilchamber 55. Meanwhile, the journal bearing portion 25 that slides on thecylinder portion 32 of the thrust collar 21 is positioned on the upperside of the circulation oil chamber 55.

The circulation oil chamber 55 includes an inner peripheral passage 56,an outer peripheral passage 57, a thrust chamber 58, and a journalchamber 59. The inner peripheral passage 56 is formed between the innerperipheral face 331 of the annular portion 33 and the oil cylinderportion 35 of the base plate 22. The outer peripheral passage 57 isformed between the outer peripheral face 332 of the annular portion 33and the middle wall 42 and lower wall 44 of the casing 24. The innerperipheral passage 56 and the outer peripheral passage 57 are formedinto an annular shape continuous in the circumferential direction of therotating shaft member 12. The thrust chamber 58 is formed between thelower end of the annular portion 33 and the base plate 22. The thrustchamber 58 accommodates the thrust bearing portion 23. The journalchamber 59 is formed between the cylinder portion 32 of the thrustcollar 21 and the inner wall 43 of the casing 24. The journal chamber 59accommodates the journal bearing portion 25.

The lubricating oil having moved from the upper oil chamber 46 to thelower oil chamber 47 through the cooling portion 26 flows into thecirculation oil chamber 55, through a lower oil groove 61 formed in thebase plate 22. The lower oil groove 61 is formed as a radially extendinggroove or an annular recess on the upper side, that is, on the casing 24side, of the base plate 22. Lubricating oil in the lower oil chamber 47passes through the lower oil groove 61 to move to the inner peripheralpassage 56 of the circulation oil chamber 55.

The lubricating oil having flowed into the circulation oil chamber 55 isreturned to the upper oil chamber 46, by use of rotation of the thrustcollar 21 inside the circulation oil chamber 55. Thus, the lubricatingoil stored in the upper oil chamber 46 is circulated through the coolingportion 26, lower oil chamber 47, lower oil groove 61, and circulationoil chamber 55. Details of the system for circulating lubricating oilwill be described later. Heat generated by sliding of the thrust bearingportion 23 and the journal bearing portion 25 is absorbed by thecirculating lubricating oil, Then, the absorbed heat is passed throughthe cooling portion 26 by circulation of the lubricating oil, and isthereby dissipated in the cooling portion 26. As a result, thelubricating oil is cooled, and cooling of the thrust bearing portion 23and journal bearing portion 25 where frictional heat is generated isprompted.

Next, the system for circulating lubricating oil from the circulationoil chamber 55 to the upper oil chamber 46 will be described in detail.

As illustrated in FIG. 4, the vertical bearing device 10 includes acirculation system part 70. The circulation system part 70 has acirculation hole 71. The circulation hole 71 is provided in the annularportion 33 of the thrust collar 21, and penetrates the annular portion33 from inner to outer sides in the radial direction, As illustrated inFIG. 5, multiple circulation holes 71 are extend radially in thecircumferential direction of the annular portion 33. In the embodiment,the annular portion 33 has 12 circulation holes 71 extending radially inthe circumferential direction. One end of the circulation hole 71 openson the outer peripheral face 332. of the annular portion 33, and theother end opens on the inner peripheral face 331 of the annular portion33. Additionally, as illustrated in FIG. 4, the circulation hole 71 istilted upward from the inner peripheral face 331 toward the outerperipheral face 332 in the radial direction of the rotating shaft member12. In other words, of the circulation hole 71, the end on the outerperipheral face 332 side is positioned higher than the end on the innerperipheral face 331 side in the axial direction of the rotating shaftmember 12, Note that the circulation hole 71 may be tilted with respectto the radial direction of the annular portion 33. Each of or each groupof the circulation hole 71 may have the same or different widths and/ororientations. Note, however, that in the context of manufacturing, it ispreferable that the circulation holes 71 all have the same width andorientation. As described above, the width and orientation of thecirculation holes 71 can be set arbitrarily to control movement oflubricating oil, depending on the required performance of the verticalbearing device 10.

Since the circulation holes 71 are provided in the annular portion 33,when the thrust collar 21 rotates together with the rotating shaftmember 12, lubricating oil on the inner peripheral side of the annularportion 33 in the circulation oil chamber 55 is guided to the outerperipheral side of the annular portion 33 by the circulation holes 71.That is, since the thrust collar 21 rotates relative to the fixed baseplate 22, the lubricating oil on the inner peripheral side of theannular portion 33 flows toward the upper oil chamber 46 through thecirculation holes 71. Thus, a flow of lubricating oil from thecirculation oil chamber 55 toward the upper oil chamber 46 is formed. Atthis time, the upward inclination of the circulation holes 71 allows thelubricating oil to be guided more smoothly toward the upper oil chamber46 on the upper side. Since the lubricating oil in the circulation oilchamber 55 flows into the upper oil chamber 46 through the circulationholes 71, the lubricating oil in the lower oil chamber 47 is supplied tothe circulation oil chamber 55 through the lower oil groove 61. Thelower oil groove 61 connects the lower oil chamber 47 and the innerperipheral passage 56 of the circulation oil chamber 55. That is, thelubricating oil stored in the lower oil chamber 47 is supplied to theinner peripheral passage 56 from the lower oil chamber 47, through thelower oil groove 61.

As described above, the outer peripheral passage 57 is formed betweenthe outer peripheral face 332 of the annular portion 33 of the thrustcollar 21 and the middle wall 42 and lower wall 44 of the casing 24. Thedistance between the outer peripheral face 332 and the casing 24 in theouter peripheral passage 57, is preferably set larger on the upper partthan in the lower part in the axial direction of the rotating shaftmember 12. To give a specific description, the lower end of thecirculation hole 71 provided in the annular portion 33 is extended toset a virtual line L. As illustrated in FIG. 6, when the lower end ofthe circulation hole 71 is extended, the virtual line L intersects withthe casing 24. With this, the outer peripheral passage 57 is formed bybeing surrounded with faces 571 and 572 which are inner walls of thecasing 24, and faces 573 and 574 which constitute the outer peripheralface 332 of the annular portion 33. In the outer peripheral passage 57,the distance between the faces 572. and 574 facing each other above thevirtual line L is set larger than the distance between the faces 571 and573 facing each other below the virtual line L. To be more specific, theouter peripheral passage 57 surrounded by the middle wall 42 and lowerwall 44 of the casing 24 and the annular portion 33 bulges toward theouter peripheral side, above an intersection point P where the outerperipheral passage 57 intersects with the virtual line L. Thus, in theouter peripheral passage 57, the distance between opposing facesincreases above the virtual line L. In addition, the casing 24 may havea curved face portion 72 on a wall face extending upward from theintersection point P. In other words, an end part on the innerperipheral side of the middle wall 42 and lower wall 44 of the casing 24may have the curved face portion 72 curving upward from the intersectionpoint P. Note that the outer peripheral passage 57 may be formed suchthat the distance between the casing 24 and the outer peripheral face332 increases continuously from lower to upper sides, in a sectionincluding the center axis of the rotating shaft member 12.

The casing 24 has a connection hole 73 in the middle wall 42 thatseparates the circulation oil chamber 55 and the upper oil chamber 46.In other words, the connection hole 73 connects the circulation oilchamber 55 and the upper oil chamber 46 by penetrating the middle wall42. The connection hole 73 has a radially outer face 731 and a radiallyinner face 732. The connection hole 73 has a lower opening 74 and anupper opening 75. The lower opening 74 is a lower end of the connectionhole 73, and opens to the outer peripheral passage 57 of the circulationoil chamber 55. The upper opening 75 is an upper end of the connectionhole 73, and opens to the upper oil chamber 46. As illustrated in FIGS.7 and 8, in the connection hole 73, it is preferable that the openingarea of the lower opening 74 be smaller than the opening area of theupper opening 75. It is also preferable that the connection hole 73 beformed into a. tapered shape where the sectional area increasescontinuously from the lower opening 74 toward the upper opening 75.

Multiple connection holes 73 are provided in the circumferentialdirection of the casing 24. In the embodiment, the casing 24 has sixconnection holes 73 in the circumferential direction. The number ofconnection holes 73 may be set arbitrarily. As illustrated in FIGS. 6and 7, for example, in the middle wall 42 in which the connection hole73 is formed, it is preferable that the face 732 on the inner peripheralside in the radial direction of the rotating shaft member 12 extendparallel to the axis of the rotating shaft member 12. That is, in theembodiment, the connection hole 73 is formed such that the innerperipheral face 732 is parallel to the center axis of the rotating shaftmember 12. Meanwhile, in the middle wall 42 in which the connection hole73 is formed, the outer peripheral face 731 in the radial direction ofthe rotating shaft member 12 is tilted relative to the center axis ofthe rotating shaft member 12 That is, in the connection hole 73, theouter peripheral face 731 is tilted in such a manner as to draw awayfrom the rotating shaft member 12 toward the upper side. Hence, theconnection hole 73 is formed into a tapered shape where the sectionalarea increases continuously from the circulation oil chamber 55 side,toward the upper oil chamber 46.

As illustrated in FIGS, 4 and 9, the vertical bearing device 10 includesa journal through hole 76. The journal through hole 76 penetrates thecylinder portion 32 of the thrust collar 21 in the radial direction. Thejournal through hole 76 connects the inner peripheral passage 56 of thecirculation oil chamber 55 and the journal chamber 59, by penetratingthe cylinder portion 32. Hence, lubricating oil in the inner peripheralpassage 56 of the circulation oil chamber 55 flows into the journalchamber 59 through the journal through hole 76. The lubricating oilhaving flowed into the journal chamber 59 is circulated into the upperoil chamber 46 from the journal chamber 59, by rotation of the thrustcollar 21. At this time, the lubricating oil having flowed into thejournal chamber 59 lubricates the journal bearing portion 25, and flowsinto the upper oil chamber 46. The journal through hole 76 may or maynot be tilted from the inner peripheral side to the outer peripheralside, in radial and axial directions of the rotating shaft member 12.Additionally, each of or each group of the journal through hole 76 mayhave the same or different widths and/or orientations. Note, however,that in the context of manufacturing, it is preferable that the journalthrough holes 76 all have the same width and orientation. As describedabove, the width and orientation of the journal through holes 76 can beset arbitrarily to control movement of lubricating oil, depending on therequired performance of the vertical bearing device 10.

The vertical bearing device 10 includes a seal member 77. The sealmember 77 is provided in a position where the upper end of the annularportion 33 of the thrust collar 21 and the lower end of the middle wall42 of the casing 24 face each other, As mentioned earlier, thecirculation oil chamber 55 includes the thrust chamber 58 thataccommodates the thrust bearing portion 23, and the journal chamber 59that accommodates the journal bearing portion 25. The lubricating oilsupplied to the circulation oil chamber 55 from the lower oil chamber 47through the lower oil groove 61, is circulated to the upper oil chamber46 through the following three circulation paths in the circulation oilchamber 55.

Path 1: circulation path starting from the inner peripheral passage 56,lubricating the thrust bearing portion 23 of the theist chamber 58, andflowing toward the upper oil chamber 46 through the outer peripheralpassage 57 and the connection hole 73

Path 2: circulation path starting from the inner peripheral passage 56,and flowing toward the upper oil chamber 46 through the circulation hole71 of the annular portion 33, the outer peripheral passage 57, and theconnection hole 73

Path 3: circulation path starting from the inner peripheral passage 56,lubricating the journal bearing portion 25 of the journal chamber 59after passing through the journal through hole 76, and flowing towardthe upper oil chamber 46

As described above, lubricating oil in the circulation oil chamber 55flows into the upper oil chamber 46 through three paths. At this time,the lubricating oil having flowed into the journal chamber 59 throughPath 3 may pass through between the upper end of the annular portion 33and the lower end of the middle wall 42 and form a flow into the outerperipheral passage 57, instead of lubricating the journal bearingportion 25 accommodated in the journal chamber 59. For this reason, theseal member 77 is provided between the upper end of the annular portion33 and the lower end of the middle wall 42. Thus, the flow oflubricating oil in Path 3 from the journal through hole 76 directedtoward the outer peripheral passage 57 is restricted by the seal member77. Conversely, the seal member 77 also restricts the lubricating oilflowing through the outer peripheral passage 57 after passing throughPath 1 or 2 from flowing into the journal chamber 59. Lubricating oilhaving passed through Path 1 and cooled the thrust bearing portion 23 ofthe thrust chamber 58 also flows through the outer peripheral passage57. The lubricating oil having passed through Path 1 is heated aftercooling the thrust bearing portion 23. If the heated lubricating oilflows into the journal chamber 59, it may hinder cooling of the journalbearing portion 25 accommodated in the journal chamber 59 by lubricatingoil. Hence, the seal member 77 is provided to restrict the flow oflubricating oil from the outer peripheral passage 57 into the journalchamber 59 as well.

The upper end of the annular portion 33 and the lower end of the middlewall 42 are also parts where the fixed casing 24 and the rotating thrustcollar 21 face each other in the axial direction of the rotating shaftmember 12. Accordingly, the seal member 77 may be a secondary thrustbearing portion that supports the thrust collar 21 in the axialdirection, together with the thrust beating portion 23. That is, theseal member 77 supports the rotating shaft member 12 in the axialdirection, together with the thrust bearing portion 23.

As illustrated in FIGS. 4 and 9, the thrust collar 21 may haveintroduction portions 78 and 79. The introduction portion 78 is providedin the inner peripheral face 331 of the annular portion 33 of the thrustcollar 21. Meanwhile, the introduction portion 79 is provided on aninner peripheral face of the cylinder portion 32 of the thrust collar21. Ends of the circulation hole 71 and the journal through hole 76 openon the inner peripheral face of the thrust collar 21. The introductionportion 78 is provided at the inner peripheral opening of thecirculation hole 71. Similarly, the introduction portion 79 is providedat the inner peripheral opening of the journal through hole 76. Theintroduction portion 78 is recessed radially outward from the innerperipheral face 331. In addition, the introduction portion 78 is formedsuch that its inner diameter gradually decreases from the innerperipheral face 331 toward the opening of the circulation hole 71.Similarly, the introduction portion 79 is recessed radially outward fromthe inner peripheral face of the cylinder portion 32. The introductionportion 79, too, is formed such that its inner diameter graduallydecreases from the inner peripheral face of the cylinder portion 32toward the opening of the journal through hole 76. The introductionportions 78 and 79 are provided in the circulation hole 71 and thejournal through hole 76 that open on the inner peripheral face of thethrust collar 21, respectively. Note that the introduction portions 78and 79 may be formed into a circumferentially continuous groove on theinner peripheral face of the thrust collar 21. In this case, each of theintroduction portions 78 and 79 is formed such that its inner diameterin the axial direction of the rotating shaft member 12 graduallydecreases toward the opening of the circulation hole 71 or the journalthrough hole 76. The groove-like part as the introduction portions 78and 79 may be formed into an annular shape continuous in thecircumferential direction of the thrust collar 21, or may bediscontinuous in the circumferential direction. Moreover, thecircumferential depth and axial width of the groove-like parts servingas the introduction portions 78 and 79 may be changed arbitrarily indifferent positions. The introduction portion 78 guides lubricating oilin the inner peripheral passage 56 into the circulation hole 71.Similarly, the introduction portion 79 guides lubricating oil in theinner peripheral passage 56 into the journal through hole 76. Thisprompts the lubricating oil in the inner peripheral passage 56 to flowinto the circulation hole 71 and the journal through hole 76. Note thatthe embodiment illustrates an example in which both of the introductionportions 78 and 79 are formed. However, the configuration may includeone or both of the introduction portions 78 and 79.

A description will be given of circulation of lubricating oil andcooling of the thrust bearing portion 23 and the journal bearing portion25 by lubricating oil, according to the vertical bearing device 10configured in the above manner.

The thrust collar 21 rotates together with the rotating shaft member 12.Accordingly, the thrust collar 21 rotates inside the fixed base plate 22and casing 24. Lubricating oil stored in the circulation oil chamber 55forms a flow directed from inner to outer sides of the rotating shaftmember 12, that is, from the inner peripheral passage 56 to the outerperipheral passage 57, due to centrifugal force and shear force causedby rotation of the thrust collar 21, or differential pressure caused bydifference in flow rate, for example. This flow causes the lubricatingoil in the inner peripheral passage 56 to circulate to the upper oilchamber 46 through the thrust chamber 58 as in the aforementioned Path1, through the circulation hole 71 as in the aforementioned. Path 2, andthrough the journal chamber 59 as in the aforementioned Path 3.

The circulation hole 71 constituting Path 2 penetrates the annularportion 33 of the thrust col lar 21, and therefore lubricating oilreceives relatively low resistance through the path. Meanwhile, thethrust chamber 58 constituting Path 1 accommodates the thrust bearingportion 23. Hence, the flow rate of lubricating oil passing through thecirculation hole 71 becomes higher than the flow rate of lubricating oilpassing through the thrust chamber 58. The lubricating oil having passedthe circulation hole 71 and having a high flow rate flows out to theouter peripheral passage 57, and its flow direction is smoothly directedupward along the curved face portion 72 formed in the casing 24. Thus,lubricating oil having flowed into the outer peripheral passage 57 fromthe circulation hole 71 changes its flow direction upward along thecurved face portion 72, and flows into the connection hole 73, At thistime, the flow rate of lubricating oil from the circulation hole 71toward the connection hole 73 is higher than the flow rate oflubricating oil from the thrust chamber 58 to the outer peripheralpassage 57. The difference in flow rate between lubricating oil flowingthrough different paths causes the lubricating oil flowing from thethrust chamber 58 to the outer peripheral passage 57 to be absorbed intolubricating oil directed from the circulation hole 71 toward theconnection hole 73. As a result, the lubricating oil passing through thethrust chamber 58 of Path 1 having a high resistance is drawn up intothe upper oil chamber 46 through the connection hole 73, by the flow oflubricating oil passing through the circulation hole 71 of Path 2.Hence, the lubricating oil having cooled the thrust bearing portion 23in the thrust chamber 58 does not accumulate in the thrust chamber 58and the outer peripheral passage 57, but is circulated to the upper oilchamber 46.

Additionally, rotation of the thrust collar 21 circulates a part oflubricating oil in the inner peripheral passage 56 to the upper oilchamber 46, through the journal through hole 76 and the journal chamber59 constituting Path 3. In this case, too, the lubricating oil in theinner peripheral passage 56 flows into the journal chamber 59 throughthe journal through hole 76, due to centrifugal force and shear forcecaused by rotation of the thrust collar 21, or differential pressurecaused by difference in flow rate, for example. The lubricating oilhaving flowed into the journal chamber 59 is caused to flow into theupper oil chamber 46 from the journal chamber 59, after lubricating oilis continuously supplied to the journal chamber 59 by rotation of thethrust collar 21. Hence, the lubricating oil having cooled the journalbearing portion 25 in the journal chamber 59 does not accumulate in thejournal chamber 59, but is circulated to the upper oil chamber 46.

The lubricating oil having returned to the upper oil chamber 46 bycirculation flows down to the lower oil chamber 47, due to gravity and apumping effect caused by circulation of the lubricating oil. At thistime, since the upper oil chamber 46 is connected to the cooling portion26, lubricating oil in the upper oil chamber 46 flows into the lower oilchamber 47 through the cooling portion 26. Although the upper oilchamber 46 is connected to the outer peripheral passage 57 of thecirculation oil chamber 55 through the connection hole 73, lubricatingoil passing through Paths 1 and 2 flow into the upper oil chamber 46through the connection hole 73, as described earlier. Hence, it isassumed that no flow of lubricating oil from the upper oil chamber 46toward the circulation oil chamber 55 through the connection hole 73will occur.

The lubricating oil having flowed into the cooling portion 26 loses heatby passing through the radiating portion 52. Specifically, thelubricating oil having absorbed the heat generated from sliding of thethrust bearing portion 23 and the journal bearing portion 25 loses heatby passing through the cooling portion 26. The cooled lubricating oilflows into the lower oil chamber 47. When the thrust collar 21 rotates,lubricating oil in the circulation oil chamber 55 flows out toward theupper oil chamber 46, as mentioned earlier. Hence, when the lubricatingoil in the circulation oil chamber 55 decreases, the lubricating oilhaving flowed into the lower oil chamber 47 is supplied to the innerperipheral passage 56 of the circulation oil chamber 55 through thelower oil groove 61.

As has been described, the thrust collar 21 rotating together with therotating shaft member 12 forms a flow of lubricating oil passing throughthe circulation oil chamber 55 and a flow of lubricating oil passingthrough the cooling portion 26, between the upper oil chamber 46 and thelower oil chamber 47. In other words, a flow of lubricating oilcirculating between the upper oil chamber 46 and the lower oil chamber47 is formed. As a result, the lubricating oil repeats cooling of thethrust bearing portion 23 and journal bearing portion 25, and the heatdissipation in the cooling portion 26. This enables lubrication andcooling of the thrust bearing portion 23 and journal bearing portion 25of the vertical bearing device 10, and heat dissipation of lubricatingoil having absorbed heat from the cooling.

In the aforementioned first embodiment, the lubricating oil passageportion 51 constituting the cooling portion 26 is exposed to theoutside. Hence, the lubricating oil flowing through the lubricating oilpassage portion 51 loses heat in the radiating portion 52 in thelubricating oil passage portion 51 exposed to the outside of the casing24. Thus, the lubricating oil having absorbed heat of the thrust bearingportion 23 and the journal bearing portion 25 is cooled in the coolingportion 26 while moving from the upper oil chamber 46 to the lower oilchamber 47. As a result, the circulating lubricating oil prompts coolingof the heated thrust bearing portion 23 and journal bearing portion 25.Additionally, the lubricating oil passage portion 51 of the coolingportion 26 is provided integrally with the casing 24, on the radiallyouter side of the casing 24. For this reason, the cooling portion 26does not require long piping. Hence, cooling capacity can be enhancedwithout complicating structure and maintenance.

Moreover, the first embodiment includes the air blowing portion 53. Theair blowing portion 53 forms a flow of air toward the cooling portion26, by the fan portion 54 that rotates together with the rotating shaftmember 12. Accordingly, cooling of the cooling portion 26 is prompted bythe flow of air formed by the fan portion 54. Hence, it is possible toprompt heat dissipation of lubricating oil circulating through thecooling portion 26, and to prompt cooling of the thrust bearing portion23 and journal bearing portion 25 by lubricating oil.

In the first embodiment, the thrust bearing portion 23 and the journalbearing portion 25 are provided in the circulation oil chamber 55,through which the lubricating oil circulating from the lower oil chamber47 to the upper oil chamber 46 flows. Hence, the thrust bearing portion23 and the journal bearing portion 25 that generate heat from supportingrotation of the rotating shaft member 12 are cooled by the lubricatingoil flowing through the circulation oil chamber 55. Accordingly, it ispossible to prompt cooling of the thrust bearing portion 23 and journalbearing portion 25, and suppress seizing. Hence, an anti-seize propertyof the vertical bearing device 10 can be improved.

Additionally, the first embodiment includes the circulation system part70. In the circulation system part 70, multiple circulation holes 71 areformed in the annular portion 33 of the thrust collar 21. When theannular portion 33 of the thrust collar 21 rotates together with therotating shaft member 12, centrifugal force and shear force, ordifferential pressure caused by difference in flow rate, for example,are generated in the lubricating oil in the circulation oil chamber 55.With this, the lubricating oil in the circulation oil chamber 55 isguided from inner to outer sides of the annular portion 33, through thecirculation holes 71 penetrating the annular portion 33. The flow oflubricating oil guided by the circulation holes 71 forms a flow oflubricating oil directed toward the upper oil chamber 46, from the loweroil chamber 47 through the circulation oil chamber 55. As a result, thelubricating oil stored in the lower oil chamber 47 is circulated to theupper oil chamber 46 through the circulation oil chamber 55, by rotationof the thrust collar 21. Accordingly, it is possible to promptcirculation of lubricating oil without using a pump device or the like.Then, the thrust bearing portion 23 and journal bearing portion 25 arelubricated and cooled by the circulating flow of lubricating oil. Hence,seizing of the thrust bearing portion 23 and journal bearing portion 25can be suppressed.

In the first embodiment, the circulation hole 71 is tilted upward frominner to outer sides. Hence, the flow of lubricating oil passing throughthe circulation hole 71 is directed upward, that is, toward the upperoil chamber 46, when the lubricating oil flows out of the circulationhole 71. This allows the lubricating oil having passed the circulationhole 71 to be easily guided to the upper oil chamber 46. Accordingly, itis possible to prompt the flow of lubricating oil having passed thecirculation hole 71, and to thereby prompt circulation of thelubricating oil. Additionally, the circulation hole 71 penetrates theannular portion 33 of the thrust collar 21. The thrust bearing portion23 is provided on the lower end of the annular portion 33. Sincelubricating oil flows through the circulation hole 71, the thrustbearing portion 23 is cooled by the lubricating oil flowing through thecirculation hole 71. Hence, it is also possible to prompt cooling of thethrust bearing portion 23 and thrust collar 21.

In the first embodiment, in the outer peripheral passage 57, thedistance between the faces 572 and 574 above the virtual line L is setlarger than the distance between the faces 571 and 573 below the virtualline L. The flow rate of lubricating oil passing through the circulationhole 71 is higher than the flow rate of lubricating oil passing throughthe thrust bearing portion 23. Hence, the flow of lubricating oilpassing through the circulation hole 71 and flowing toward the upper oilchamber 46 draws up the lubricating oil passing through the thrustbearing portion 23. As a result, on the upper side of the virtual lineL, lubricating oil having passed through the thrust bearing portion 23flows together with lubricating oil having passed through thecirculation hole 71 For this reason, the distance is increased on theupper side of the virtual line so that the lubricating oil having anincreased flow rate does not accumulate and flows toward the upper oilchamber 46. Hence, it is possible to prompt circulation of lubricatingoil.

In the first embodiment, the casing 24 has the curved face portion 72 ona wall face provided higher than the intersection point P with thevirtual line L. Lubricating oil having flowed out of the circulationhole 71 is guided smoothly by the curved face portion 72, to the upperoil chamber 46 on the upper side. Accordingly, resistance in thecirculation path of lubricating oil is reduced, and circulation of thelubricating oil can be prompted.

In the first embodiment, the connection hole 73 provided in the middlewall 42 of the casing 24 connects the circulation oil chamber 55 and theupper oil chamber 46. The connection hole 73 is formed into a taperedshape whose sectional area increases continuously toward the upper oilchamber 46, from the outer peripheral passage 57 side of the circulationoil chamber 55. Hence, the lubricating oil on the circulation oilchamber 55 side is guided by the connection hole 73 having theincreasing sectional area, and is moved to the upper oil chamber 46.Accordingly, it is possible to prompt circulation of lubricating oilwithout increasing resistance.

In the first embodiment, the inner peripheral face 732 of the connectionhole 73 is parallel to the center axis of the rotating shaft member 12.Accordingly, a flow directed toward the upper oil chamber 46 on theupper side is formed in the lubricating oil passing through theconnection hole 73, and therefore the flow is less likely to bedisturbed. Hence, it is possible to suppress increase in resistance dueto flow disturbance, and to prompt circulation of lubricating oil.

The first embodiment includes the seal member 77, The seal member 77restricts the flow of lubricating oil between the outer peripheralpassage 57 and the journal chamber 59. If lubricating oil flows from thejournal chamber 59 to the outer peripheral passage 57, lubrication ofthe journal bearing portion 25 accommodated in the journal chamber 59may become insufficient. On the other hand, if lubricating oil flowsfrom the outer peripheral passage 57 to the journal chamber 59, thelubricating oil heated from cooling the thrust bearing portion 23 mayflow into the journal bearing portion 25 and raise the temperature ofthe journal bearing portion 25. Hence, by providing the seal member 77,the flow of lubricating oil between the outer peripheral passage 57 andthe journal chamber 59 can be blocked. It is therefore possible toprompt circulation of lubricating oil without hindering lubrication andcooling of the journal beating portion 25.

In the first embodiment, the seal member 77 may serve as a secondarythrust bearing portion. In this configuration, the rotating shaft member12 is supported by the seal member 77 serving as the thrust bearingportion 23 and the secondary thrust bearing portion. Hence, it ispossible to more stably support the rotating shaft member 12 and promptcirculation of lubricating oil, without increasing the number of parts.

The first embodiment includes the introduction portion 78 to the inletof the circulation hole 71, and the introduction portion 79 to the inletof the journal through hole 76. The introduction portions 78 and 79 areset such that their inner diameter decrease toward the circulation hole71 and the journal through hole 76. With this, the introduction portions78 and 79 guide lubricating oil in the inner peripheral passage 56 tothe circulation hole 71 and the journal through hole 76. In other words,the lubricating oil in the inner peripheral passage 56 is guided bythese introduction portions 78 and 79 to be introduced into thecirculation hole 71 and journal through hole 76. This prompts the flowof lubricating oil from the inner peripheral passage 56 to thecirculation hole 71 and the journal through hole 76. Hence, it ispossible to prompt circulation of lubrication oil.

Modification of First Embodiment

In the aforementioned first embodiment, in the connection hole 73,tilted faces tilt in opposite directions relative to the circumferentialdirection of the casing 24, so as to be symmetric to each other, asillustrated in FIGS. 7 and 8. However, the connection hole 73 may beconfigured such that the tilted faces tilt in the same directionrelative to the circumferential direction, as illustrated in FIG. 10. Ifthe rotating shaft member 12 is configured to rotate both in the normaland reverse directions, it is preferable that the connection hole 73 beformed into the shape illustrated in FIGS. 7 and 8. Additionally, thefront and rear inclinations of the connection hole 73 in thecircumferential direction of the casing 24 may be the same asillustrated in FIGS. 8 and 10, or may be different as illustrated inFIG. 11. In both cases, the shape of the connection hole 73 can be setarbitrarily to control movement of lubricating oil, depending on therequired performance of the vertical bearing device 10.

Second Embodiment

FIG. 12 illustrates a vertical bearing device of a second embodiment.

FIG. 12 is a cross-sectional view in which a casing 24 is cut in anintermediate part thereof in the axial direction, and from which amiddle wall 42, an inner wall 43, and other parts are omitted. In thesecond embodiment, a casing main body 41 constituting an outer wall ofthe casing 24 has a plane portion 81 extending flat in thecircumferential direction. That is, the casing main body 41 has theplane portion 81 flat in the circumferential direction, and an annularportion 82 that connects the plane portions 81 in the circumferentialdirection. The annular portion 82 is formed into an annular shape thatis concentric with the rotating shaft member 12. That is, the annularportion 82 is formed into a curved face that is arc shaped in sectionssuch as those illustrated in FIG. 12. In the second embodiment, thecasing main body 41 has two plane portions 81 and two annular portions82

In the second embodiment, a cooling portion 26 is provided on the planeportion 81 of the casing main body 41. That is, a lubricating oilpassage portion 51 constituting the cooling portion 26 is exposed to theoutside of the casing main body 41 from the plane portion 81, in thecasing main body 41. In addition, a radiating portion 52 constitutingthe cooling portion 26 is provided in a position facing the planeportion 81. The two cooling portions 26 of the second embodiment arerespectively provided on the two plane portions 81 of the casing mainbody 41.

By providing the cooling portion 26 on the plane portion 81 as in thesecond embodiment, an air flow formed by a fan portion 54 flows evenlyinto a gap between the cooling portion 26 and the plane portion 81. Whenthe planar cooling portion 26 is provided on the arc-shaped casing mainbody 41 as in the aforementioned first embodiment, the distance betweenthe cooling portion 26 and the casing main body 41 varies in thecircumferential direction of the casing main body 41. That is, when thearc-shaped casing main body 41 and the planar cooling portion 26 faceeach other, the distance between the casing main body 41 and the coolingportion 26 is larger on both end sides in the circumferential directionof the casing main body 41. On the other hand, the distance between thecasing main body 41 and the cooling portion 26 is smaller in a middlepart in the circumferential direction of the casing main body 41. Thus,when the arc-shaped casing main body 41 and the planar cooling portion26 face each other, the sectional area through which air generated bythe fan portion 54 passes through varies in the circumferentialdirection of the casing main body 41. Meanwhile, in the secondembodiment, the cooling portion 26 and the plane portion 81 are arrangedsubstantially parallel to each other. Hence, the sectional area of thespace through which air passes is substantially even in thecircumferential direction of the casing main body 41. With this, the airflow formed by the fan portion 54 passes through the cooling portion 26evenly. Consequently, cooling efficiency of the cooling portion 26 canbe enhanced.

Additionally, in the second embodiment, the cooling portion 26 isattached to the planar plane portion 81 in the casing main body 41.Hence, work for positioning and fixing the cooling portion 26 is madesimpler than when providing it on the curved annular portion 82. As aresult, it is possible to improve work efficiency in assembling thecooling portion 26 onto the casing main body 41.

As has been described, in the second embodiment, the plane portion 81 isformed in the casing main body 41, and the cooling portion 26 isprovided on the plane portion 81. Hence, the flow of cooling air formedby the fan portion 54 passes through the cooling portion 26 evenly,Accordingly, cooling efficiency of the cooling portion 26 is improved,and the cooling portion 26 can be downsized.

Moreover, in the second embodiment, the cooling portion 26 is providedon the flat plane portion 81, so that workability of assembling thecooling portion 26 onto the casing main body 41 can also be improved.

Modification of Second Embodiment

The second embodiment illustrated in FIG. 12 describes an example offorming two plane portions 81 in the casing main body 41, and providingthe cooling portions 26 on each of the two plane portions 81.

However, the casing main body 41 may have three plane portions 81 asillustrated in FIG. 13. In a vertical bearing device 10 illustrated inFIG. 13, a cooling portion 26 may be provided on each of the three planeportions 81. Instead, a casing main body 41 may have four plane portions81 as illustrated in FIG. 14, or may be configured only of planeportions 81, as illustrated in FIG. 15.

Thus, any number of plane portions 81 may be provided in the casing mainbody 41. Then, by providing the cooling portion 26 on all or any of theplane portions 81, more cooling portions 26 can be provided, and coolingefficiency can be improved even more. Additionally, as has beendescribed in the second embodiment, since the cooling portion 26 isprovided on the plane portion 81, attachment of the cooling portion 26onto the casing main body 41 is made easier. Hence, even when morecooling portions 26 are provided to improve cooling efficiency,attachment of the cooling portion 26 onto the plane portion 81 candrastically reduce man-hours.

Third Embodiment

FIG. 16 illustrates a vertical bearing device of a third embodiment.

In the third embodiment, a radiating portion 52 of a cooling portion 26is tilted relative to the axial direction of a rotating shaft member 12.In other words, the radiating portion 52 is not parallel to the rotatingshaft member 12, but is tilted relative thereto. When the radiatingportion 52 is provided parallel to the rotating shaft member 12, thatis, provided as in the first embodiment, a flow of air formed by a fanportion 54 passes through between the radiating portion 52 and a casingmain body 41 in the axial direction. Then, the flow of cooling airhaving passed through between the radiating portion 52 and the casingmain body 41 is curved radially outward by the base plate 22. For thisreason, the air flow formed by the fan portion 54 is more likely to flowon the lower side of the radiating portion 52 than on the upper sidethereof. Accordingly, lubricating oil is cooled mainly on the lower sideof the radiating portion 52, and a radiating surface of the radiatingportion 52 cannot be fully used in many cases.

Hence, by tilting the radiating portion 52 as in the third embodiment,the air flow formed by the fan portion 54 can be spread more easily overthe entire radiating portion 52. In other words, the air flow formed bythe fan portion 54 is more likely to flow into the entire radiatingportion 52 than when the radiating portion 52 is parallel to the axis.Hence, it is possible to prompt cooling of lubricating oil withoutexpanding the area of the radiating portion 52. Accordingly, coolingefficiency of the radiating portion 52 can be improved.

Incidentally, the radiating portion 52 may be provided perpendicular tothe axial direction of the rotating shaft member 12, as illustrated inFIG. 17. In other words, the radiating portion 52 forms a 90-degreeangle with the rotating shaft member 12. By thus arranging the radiatingportion 52 perpendicular to the axis of the rotating shaft member 12,the air flow formed by the fan portion 54 passes through the entireradiating portion 52 substantially evenly. Hence, it is possible toprompt cooling of lubricating oil without expanding the area of theradiating portion 52. Accordingly, cooling efficiency of the radiatingportion 52 can be improved even more.

Fourth Embodiment

FIG. 18 illustrates a vertical bearing device of a fourth embodiment.

In the fourth embodiment, a cooling portion 26 has a straightening vane91. The straightening vane 91 is provided on an inlet side, where airflows into a radiating portion 52 from a fan portion 54. In the fourthembodiment, the straightening vane 91 is provided in a lubricating oilpassage portion 51 connected to an upper oil chamber 46. Specifically,the straightening vane 91 is provided in a part where the lubricatingoil passage portion 51 extending from the upper oil chamber 46 connectsto the radiating portion 52. By providing the straightening vane 91, anair flow formed by the fan portion 54 is aligned by the straighteningvane 91. That is, the straightening vane 91 cancels disturbance in theair flow formed by the fan portion 54, and guides a stable air flow toenter the radiating portion 52. Hence, a less disturbed air flow passesthrough the radiating portion 52.

In the fourth embodiment, the air flow formed by the fan portion 54 isaligned by the straightening vane 91, and is guided to the radiatingportion 52. With this, the flow of air passing through the radiatingportion 52 is stabilized. Hence, cooling efficiency can be improved.

Fifth Embodiment

FIG. 19 illustrates a vertical bearing device of a fifth embodiment.

A vertical bearing device 10 of the fifth embodiment includes ashielding plate 92. The shielding plate 92 is provided between a coolingportion 26 and a casing 24. The shielding plate 92 blocks transmissionof heat from the cooling portion 26 to the casing 24. When the radiatingportion 52 is tilted relative to the axis of the rotating shaft member12 as in the third embodiment illustrated in FIGS. 16 and 17, thedistance between the radiating portion 52 and the casing 24 is reducedin some parts, When the radiating portion 52 and the casing 24 thus comeclose, heat may be transmitted from the heated radiating portion 52 tothe casing 24. For this reason, the shielding plate 92 is providedbetween the radiating portion 52 and the casing 24, With this, heat ofthe radiating portion 52 is shielded by the shielding plate 92, andtransmission thereof to the casing 24 can be suppressed.

In the fifth embodiment, the shielding plate 92 is provided to suppresstransmission of heat from the radiating portion 52 to the casing 24.Accordingly, it is possible to suppress deterioration in coolingcapacity, even when the tilted radiating portion 52 is brought close tothe casing 24.

Sixth Embodiment

FIG. 20 illustrates a vertical bearing device of a sixth embodiment.

In the sixth embodiment, a cooling portion 26 has a lubricating oilpassage portion 51, and multiple radiating portions 52. The lubricatingoil passage portion 51 is exposed to the outside of a casing main body41 from an upper oil chamber 46, and consecutively passes throughmultiple radiating portions 52 before connecting to a lower oil chamber47. That is, the lubricating oil passage portion 51 consecutively passesthrough multiple serially-arranged radiating portions 52. Hence,lubricating oil having flowed into the lubricating oil passage portion51 from the upper oil chamber 46 passes through the serial radiatingportions 52, and is thereby cooled in multiple steps. Then, thelubricating oil cooled by the multiple radiating portions 52 flows intothe lower oil chamber 47.

In the sixth embodiment, cooling of the lubricating oil flowing throughthe lubricating oil passage portion 51 is prompted, by allowing thelubricating oil to consecutively pass through multiple radiatingportions 52. Then, in the sixth embodiment, even when multiple radiatingportions 52 are provided, only two holes, which are an inlet and anoutlet, need to be formed in the casing main body 41 to allow passage ofthe lubricating oil. For example, when the radiating portion 52 isarranged in front of each of six plane portions 81 provided in thecasing main body 41, six lubricating oil passage portions 51 need to beconnected to the casing main body 41. In this case, two holes for onelubricating oil passage portion 51, that is, a total of 12 holes need tobe formed in the casing main body 41 to allow passage of the lubricatingoil. Meanwhile, in the sixth embodiment, even when six radiatingportions 52 are provided, only two lubricating oil passage portions 51are used, and therefore, a total of four holes are formed in the casingmain body 41. Thus, in the sixth embodiment, less holes need to beformed in the casing main body 41 to allow passage of lubricating oil.This reduces man-hours and required parts of the casing main body 41.Hence, the structure can be simplified while maintaining the coolingcapacity.

Other Embodiments

The present invention described above is not limited to the aboveembodiments, and is applicable to various embodiments without departingfrom the gist of the invention.

The third embodiment describes a configuration in which the radiatingportion 52 is tilted to widen the upper side in the axial direction ofthe rotating shaft member 12. However, reversely, the radiating portion52 may be tilted to widen the lower side in the axial direction of therotating shaft member 12. In this case, it is preferable that theshielding plate 92 of the fourth embodiment be provided on the upperside of the radiating portion 52 that comes close to the casing mainbody 41. Moreover, the connection between the radiating portion 52 andthe lubricating oil passage portion 51 is not limited to the aboveexamples. For example, in the example of FIG. 17, the lubricating oilpassage portion 51 connects to the radially outer side of the radiatingportion 52 from the upper oil chamber 46, and connects to the lower oilchamber 47 from the radially inner side of the radiating portion 52. Incontrast, the lubricating oil passage portion 51 may connect to theradially inner side of the radiating portion 52 from the upper oilchamber 46, and connect to the lower oil chamber 47 from the radiallyouter side of the radiating portion 52. Additionally, the flow oflubricating oil may be clockwise or anticlockwise, around the rotatingshaft member 12. Thus, connection between the radiating portion 52 andthe lubricating oil passage portion 51, and the direction of flow oflubricating oil may be changed arbitrarily, depending on the usage ofthe applied radiating portion 52.

In addition, the aforementioned multiple embodiments describe an examplein which lubricating oil passing through the radiating portion 52through the lubricating oil passage portion 51 flows from the upper oilchamber 46 to the lower oil chamber 47. On the other hand, in anotherconceivable configuration, lubricating oil passing through the radiatingportion 52 through the lubricating oil passage portion 51 may flow fromthe lower oil chamber 47 to the upper oil chamber 46. In this case,lubricating oil passing through the radiating portion 52 flows from thelower oil chamber 47 to the upper oil chamber 46, by a pumping effectusing centrifugal force and shear force generated in the lubricating oilby rotation of the thrust collar 21. Thus, the path and direction inwhich lubricating oil flows in the lubricating oil passage portion 51may be set arbitrarily, as long as the lubricating oil passes throughthe radiating portion 52.

Moreover, the aforementioned multiple embodiments describe an example inwhich the plane portion 81 is provided in the casing main body 41 forattachment of the cooling portion 26. However, as illustrated in FIG.21, the cooling portion 26 does not necessarily have to be attached onthe plane portion 81 of the casing main body 41. That is, the casingmain body 41 may have a plane portion 81 that does not have the coolingportion 26 attached thereon.

The invention claimed is:
 1. A vertical bearing device comprising: acylindrical thrust collar that rotates together with a rotating shaftmember extending in the direction of gravitational force; a base platethat faces the lower end of the thrust collar; a thrust bearing partthat is provided in a part where the thrust collar and the base plateface each other in an axial direction of the rotating shaft member, andsupports the rotating shaft member in the axial direction; a casing thatsurrounds the outer peripheral side of the rotating shaft member, isformed into a container shape integrally forming, with the base plate,an oil chamber for storing lubricating oil, and partitions the oilchamber into an upper oil chamber provided on the upper side and a loweroil chamber provided on the lower side in the direction of gravitationalforce; a journal bearing part that is provided in a part where thecasing and the thrust collar face each other in a radial direction ofthe rotating shaft member, and supports the rotating shaft member in theradial direction; a cooling part that has a lubricating oil passage partprovided integrally with the casing on the radially outer side of thecasing, and exposed from the casing to allow passage of the lubricatingoil moving from the upper oil chamber to the lower oil chamber, andcools the lubricating oil moving from the upper oil chamber to the loweroil chamber through the lubricating oil passage part by air on the outerperipheral side of the casing; and a shielding plate that is providedbetween the cooling part and the casing, and blocks transmission of heatfrom the cooling part to the casing.
 2. The vertical bearing deviceaccording to claim 1, further comprising an air blowing part thatrotates integrally with the rotating shaft member, and forms a flow ofair toward the cooling part.
 3. The vertical bearing device according toclaim 1, wherein: the casing partitions the oil chamber not only intothe upper oil chamber and the lower oil chamber, but also into acirculation oil chamber that allows passage of the lubricating oilcirculating from the lower oil chamber to the upper oil chamber byrotation of the thrust collar rotating together with the rotating shaftmember; and the thrust bearing part and the journal bearing part areprovided in the circulation oil chamber.
 4. The vertical bearing deviceaccording to claim 1, wherein: the casing has a casing main body thatconstitutes an outer wall; the casing main body has a plane part that isflat in the circumferential direction; and the cooling part is providedin the plane part.
 5. The vertical bearing device according to claim 1,wherein the cooling part is tilted relative to the axial direction ofthe rotating shaft member.
 6. The vertical bearing device according toclaim 1, wherein the cooling part has a straightening vane that alignsan air flow entering the cooling part.
 7. The vertical bearing deviceaccording to claim 1, wherein: the cooling part has a plurality ofradiating parts that allows lubricating oil flowing through thelubricating oil passage part to lose heat; and the lubricating oilpassage part consecutively passes through the plurality of radiatingparts.
 8. A rotary machine comprising: the vertical bearing deviceaccording to claim 1; and a rotor that has at least one end in the axialdirection of the rotating shaft member supported by the vertical bearingdevice.
 9. A vertical bearing device comprising: a cylindrical thrustcollar that rotates together with a rotating shaft member extending inthe direction of gravitational force; a base plate that faces the lowerend of the thrust collar; a thrust bearing part that is provided in apart where the thrust collar and the base plate face each other in anaxial direction of the rotating shaft member, and supports the rotatingshaft member in the axial direction; a casing that surrounds the outerperipheral side of the rotating shaft member, is formed into a containershape integrally forming, with the base plate, an oil chamber forstoring lubricating oil, and partitions the oil chamber into an upperoil chamber provided on the upper side and a lower oil chamber providedon the lower side in the direction of gravitational force; a journalbearing part that is provided in a part where the casing and the thrustcollar face each other in a radial direction of the rotating shaftmember, and supports the rotating shaft member in the radial direction;and a cooling part that has a straightening vane that aligns an air flowentering the cooling part and a lubricating oil passage part providedintegrally with the casing on the radially outer side of the casing, andexposed from the casing to allow passage of the lubricating oil movingfrom the upper oil chamber to the lower oil chamber, and cools thelubricating oil moving from the upper oil chamber to the lower oilchamber through the lubricating oil passage part by air on the outerperipheral side of the casing.
 10. A vertical bearing device comprising:a cylindrical thrust collar that rotates together with a rotating shaftmember extending in the direction of gravitational force; a base platethat faces the lower end of the thrust collar; a thrust bearing partthat is provided in a part where the thrust collar and the base plateface each other in an axial direction of the rotating shaft member, andsupports the rotating shaft member in the axial direction; a casing thatsurrounds the outer peripheral side of the rotating shaft member, isformed into a container shape integrally forming, with the base plate,an oil chamber for storing lubricating oil, and partitions the oilchamber into an upper oil chamber provided on the upper side and a loweroil chamber provided on the lower side in the direction of gravitationalforce; a journal bearing part that is provided in a part where thecasing and the thrust collar face each other in a radial direction ofthe rotating shaft member, and supports the rotating shaft member in theradial direction; and a cooling part that has a lubricating oil passagepart provided integrally with the casing on the radially outer side ofthe casing, and exposed from the casing to allow passage of thelubricating oil moving from the upper oil chamber to the lower oilchamber, and cools the lubricating oil moving from the upper oil chamberto the lower oil chamber through the lubricating oil passage part by airon the outer peripheral side of the casing; the cooling part having aplurality of radiating parts that allows lubricating oil flowing throughthe lubricating oil passage part to lose heat, and the lubricating oilpassage part consecutively passing through the plurality of radiatingparts.